Method for measuring the absolute steering angle of steering shaft for vehicle

ABSTRACT

An absolute steering angle of a steering shaft for a vehicle is measured using rotatable bodies that rotate together with the steering shaft at respective predetermined rotation ratios. A Ψ M ′ value is obtained by measuring a relative rotational angle Ψ′ of a first rotatable body and a θ M ′ value is obtained by measuring the relative rotational angle θ′ of a second rotatable body. θ C &#39;s are obtained by calculating relative rotational angles θ&#39;s of the second rotatable body corresponding to the Ψ M ′ value, using the relation between Ψ′ and θ′. A frequency i-value of the first rotatable body is obtained by comparing the θ C s to the θ M ′ value. An absolute steering angle Φ 1  of the steering shaft is obtained based on the relation between absolute rotational angles Ψ and Φ, after Ψ is obtained using the i-value.

RELATED APPLICATIONS

The present disclosure relates to subject matter contained in priority Korean Application No. 10-2003-0079320, filed on Nov. 11, 2003, which is herein expressly incorporated by reference in its entirety.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to a method for measuring an absolute steering angle of a steering shaft for a vehicle, and more specifically, to a method for measuring an absolute steering angle of a steering shaft by using two rotatable bodies that rotate together with the steering shaft at a predetermined rotation ratio.

2. Description of the Related Art

In general, measurement of an absolute steering angle of a steering shaft using an angle sensor only is known to be difficult because the measurement range is greater than 360°.

Also the steering angle of the steering shaft should be immediately measured following start-up of a vehicle, regardless of an initial angular position. However, a prior steering angle would not be used to measure a relative change at present stage.

U.S. Pat. Nos. 5,930,905 and 6,466,889B1 disclose a method for measuring an absolute steering angle of a steering shaft based on rotational angular measurements of a first rotatable body and a second rotatable body that rotate together with a steering shaft at a predetermined rotation ratio.

In the disclosures, the absolute rotation angle of the first rotatable body and of the second rotatable body are expressed by Ψ=Ψ′+iΩ and θ=θ′+jΩ, respectively (wherein, Ω indicates a measurement range of an angle sensor measuring the Ψ′ and the θ′; i is a whole number representing the number of times when the first rotatable body's absolute rotation angle Ψ is greater than the Ω, i.e. a frequency of the first rotatable body; and j is a frequency of the second rotatable body), and the absolute steering angle, Φ, can be obtained through a specific calculation procedure using measurements of ψ′ and θ′.

According to the U.S. Pat. No. 5,930,905, the measurements of Ψ′ and θ′ are substituted to the following equation (1), which is derived from a geometrical relation among Ψ, θ, and Φ to get k, and by rounding off k, a whole number k is obtained. Then the k, Ψ′ and θ′ are substituted to the following equation (2) to obtain Φ. k={(m+1)Θ′−mΨ′}/Ω  <Equation 1> Φ={mΨ′+(m+1)Θ′−(2m+1)kΩ}/2n  <Equation 2>

(Here, m indicates the number of gear teeth of the first rotatable body; m+1 indicates the number of gear teeth of the second rotatable body; and n indicates the number of gear teeth formed on the steering shaft engaged with the first and second rotatable bodies.)

On the other hand, according to the U.S. Pat. No. 6,466,889B 1, the steering angle, Φ, can be obtained directly from a relation between the difference of absolute rotation angles of two rotatable bodies, Ψ−θ, and ‘i’ of the first rotatable body (or ‘j’ of the second rotatable body). Here, Ψ−θ is obtained by adding Ω to a measurement of Ψ′−θ′ if the measurement is a negative value, or by applying a measurement of Ψ−θ′if the measurement is not a negative value. The ‘i’ is calculated from the relation between Ψ−θ , and i. Ψ is calculated from the known values of Ψ′ and i. Based on these values, the absolute steering angle of a steering shaft, Φ, is obtained.

When ‘i’ becomes k1 as the steering shaft is fully rotated, the rotation angle difference Ψ−θ should be equal or less than the measurement range of the angle sensor, namely Ω (cf. in the U.S. Pat. No. 6,466,889B1, Ψ−θ is set to be equal to Ω). In other words, the rotation angle difference Ψ−θ successively varies from 0° to Ω until the steering shaft is fully rotated, and i-value varies step by step from 0 to k1.

In particular, the U.S. Pat. No. 6,466,889B1 made an assumption that Ψ−θ and i-value are in a linearly proportional relation with each other, meaning that the value for i successively varies from 0 to k1 as the rotation angle difference Ψ−θ successively varies from 0° to Ω. Also, the value of ‘i’ is obtained by taking a maximum whole number that is smaller than a value obtained from the multiplication of Ψ−θ measured value and k1/Ω. For example, if ψ−θ times k1/Ω is 5.9, i is 5.

However, the above method poses a problem that ‘i−j’ has to be either 0 or 1 and should not be greater than 2 because a maximum value of Ψ−θ cannot be greater than Ω.

SUMMARY OF THE INVENTION

It is, therefore, an object of the present invention to provide a method for measuring an absolute steering angle of a steering shaft rotating by more than 360 degrees, to reduce measurement errors and to simplify a calculation procedure.

Another object of the present invention is to provide a method for measuring an absolute steering angle of a steering shaft which can obtain the frequency of the first rotatable body, i, or the frequency of the second rotatable body, j, without knowing Ψ−θ. After being once obtained, i or j can subsequently be obtained through a simple calculation procedure.

As for the method for measuring the steering angle of the steering shaft for a vehicle, a first rotatable body that rotates together with the steering shaft at an r1 ratio, and a second rotatable body that rotates together with the steering shaft at an r2 ratio are used.

An absolute rotational angle of the first rotatable body, Ψ, can be expressed as Ψ′+iΩ, and an absolute rotational angle of the second rotatable body, θ, can be expressed as θ′+iΩ. Ψ′ and θ′ are measured by means of angle sensors. Here, Ω represents the measurement ranges of the angle sensors, i is a whole number that represents a frequency of the first rotatable body indicating the number of times the first rotatable body ratates over Ω(for example, if Ψ is 380° in the case that Ω is 180°, then i is 2), and j is a frequency of the second rotatably body. In other words, the absolute rotational angle of the first rotatable body, Ψ, can be expressed by Ψ′+iΩ, wherein Ψ′ is a relative rotational angle measured by the angle sensor whose measurement range is Ω. The absolute rotational angle of the second rotatable body, θ, can be expressed in the same manner.

The measurement range of the angle sensor, Ω, could be 180° or 360° or a different degree. Either contact angle sensors or non-contact angle sensors can be utilized as long as the angle sensors are suitable for the measurement of Ψ′ and θ′.

In the present invention, Ψ′ and θ′ measurements, i.e. Ψ_(M)′ and θ_(M)′, are obtained by using the angle sensors whose measurement ranges are Ωs. Then, based on a relation between Ψ′ and θ′, a plurality of θ's corresponding to the Ψ_(M)′ is calculated to obtain their calculation values θ_(C)′. By comparing the plurality of θ_(C)′to the θ_(M)′, the frequency of the first rotatable body, i, is obtained. By using this i-value, the absolute rotational angle of the first rotatable body, Ψ, is obtained. Finally, the steering angle Φ (hereinafter, the resulting Φ is called Φ1) of the steering shaft is obtained from the relation between Ψ and θ.

Although the frequency of the first rotatable body, i, can be obtained through the above procedure every time the steering angle Φ of the steering shaft is obtained by measuring Ψ_(M)′ and θ_(M)′, it is more preferable to utilize the already obtained i-value. That is, after comparing a present Ψ_(M)′ value to a previous Ψ_(M)′ value, and add/subtract 1 to/from a previous i-value. The reason for that is when the i-value is increased by as much as 1, the value of Ψ_(M)′ varies from Ω to 0, and when the i-value is decreased by as much as 1, the value of Ψ_(M)′ varies from 0 to Ω. That is to say, Ψ_(M)′ varies a lot before and after a variation of the i-value. The above procedure is useful not only for simplifying the calculation procedure, but also for freeing the influence of a measurement error included in θ_(M)′ upon the i-value.

More preferably, based on a relation between Ψ′ and θ′, a plurality of Ψ's corresponding to the θ_(M)′ are calculated to obtain their calculation values Ψ_(C)′. By comparing the plurality of Ψ_(C)'s to the Ψ_(M)′, the frequency of the second rotatable body, j, is obtained. By using this j-value, the absolute rotational angle of the second rotatable body, θ, is obtained. In this manner, the steering angle Φ (hereinafter, the resulting Φ is called Φ2) of the steering shaft is additionally obtained from the relation between θ and Ψ. Finally, the mean value of the Φ1 and the Φ2 is taken to define the steering angle, Φ, of the steering shaft. By taking the mean value, the measurement errors included in Ψ_(M)′ and θ_(M)′ can be cancelled out. In the ideal case without any measurement error, the Φ1 value and the Φ2 value are equal, but, in reality, the Φ1 value and the Φ2 value are not equal.

Similar to the above-described method for obtaining an i-value, it is more preferable to get a present j-value by adding/subtracting 1 to/from a previous j-value based on a comparison of a previous θ_(M)′ value to a present θ_(M)′ value. If the resulting Φ1 value and the Φ2 value are too much different from each other, Ψ_(C)′ and θ_(C)′are recalculated, and Ψ_(M)′ and θ_(M)′ are compared again to get a new i-value and a new j-value again.

BRIEF DESCRIPTION OF THE DRAWINGS

The above objects, features and advantages of the present invention will become more apparent from the following detailed description when taken in conjunction with the accompanying drawings, in which:

FIG. 1 illustrates a preferred embodiment of the present invention;

FIG. 2 graphically illustrates a relation between Ψ′ and θ′ in accordance with a steering angle of a steering shaft;

FIG. 3 illustrates a calculation procedure to obtain φ1 according to the present invention; and

FIG. 4 illustrates a simplified calculation procedure for obtaining ‘i’ according to the present invention.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

A preferred embodiment of the present invention will be described herein below with reference to the accompanying drawings. In the following description, well-known functions or constructions are not described in detail since they would obscure the invention in unnecessary detail.

FIG. 1 shows a first rotatable body 2 and a second rotatable body 3 being engaged with a steering shaft 1, angle sensors 4 and 5 for measuring relative rotation angles Ψ′ and θ′ of the first and second rotatable bodies, and an operational circuit 6 for conducting a designated operation using Ψ′_(M) and θ′_(M) measurements provided by the sensors 4 and 5 and for outputting a resulting Φ. Here, a rotation ratio (r1) of the steering shaft to the first rotatable body is 7/4, and a rotation ratio (r2) of the steering shaft to the second rotatable body is 6.5/4 (the numbers of the teeth of the gears represented in FIG. 1 may not be correct). FIG. 2 graphically shows a relation between a relative rotation angle (Ψ′) of the first rotatable body and a relative rotation angle (θ′) of the second rotatable body during 4 rotations of the steering shaft. In FIG. 2, x-axis denotes the steering angle Φ, and Ω is 180°. FIG. 3 illustrates a calculation procedure for obtaining an absolute steering angle, Φ, of a steering shaft, based on measurements of the Ψ′ and the θ′.

Preferably, the relation between the relative rotation angles of the first and second rotatable bodies is obtained experimentally by measuring the relative rotation angle (ψ′) of the first rotatable body and the relative rotation angle (θ′) of the second rotatable body, as varing the steering angle of the steering shaft.

As shown in FIG. 3, ψ_(M)′ and θ′_(M) are measured by angle sensors. Then by taking advantage of the relation shown FIG. 2, a plurality of θ_(C)'s corresponding the ψ_(M)′are calculated (θ_(C)i′ in FIG. 3 indicates θ_(C)′ corresponding to ‘i’). Then the closest value among the θ_(C)'s to θ_(M)′ is found to get i. For instance, suppose that Ψ_(M)′=130°, and θ′₌₁₀₅°. As shown on the graph of FIG. 2, when Ψ′=130°, its corresponding θ_(C)'s, given that i ranges from 0 to 13, are 120.7°, 107.9°, 95°, 82.1°, 69.3°, 56.4°, 43.6°, 30.7°, 17.9°, 5°, 172.1°, 159.3°, 146.4°, and 133.6°, successively. Among these values for θ_(C)'s, 107.9° is the closest to the θ_(M)'s, which is 105°, so the corresponding i becomes 1.

Using the known i-value and Ψ_(M)′ values, the steering angle, Φ1, of the steering shaft can be calculated applying the following equation 5. Φ1=1/r 1 (Ψ_(M) ′+iΩ)=4/7(130°+180°)=177°.  <Equation 5>

Although the ‘i’ value can be obtained using the above equation every time, it is more preferable to utilize the already obtained i-value. That is, after comparing a present Ψ_(M)′ value to a previous Ψ_(M)′ value, and add/subtract 1 to/from a previous i-value. For example, if ΔΨ_(M)′ (i.e. the present Ψ_(M)′ value−the previous Ψ_(M)′ value) is smaller than a predetermined negative value, add 1 to the previous i-value, and if ΔΨ_(M)′ is larger than the predetermined positive value, subtract 1 from the previous i-value, if ΔΨ_(M)′ belongs to neither case, the previous i-value is kept as the present i-value.

The above procedure is well illustrated in FIG. 4. As shown in FIG. 4, if ΔΨ_(M)′ is smaller than a determined value, say,—As, 1 is added to the previous i-value, and if ΔΨ_(M)′ is larger than As, 1 is subtracted from the previous i-value, and in neither case, the present i-value maintains as the present i-value. For instance, suppose that the previous i-value is 3, the specific value As is 170°, the previous Ψ_(M)′ value is 179°, and the present Ψ_(M)′ value is 1°. Then the ΔΨ_(M)′ equals to −178°, which is smaller than −170°, so the present i-value becomes 4. On the other hand, if the previous Ψ_(M)′ value is 1° and the present Ψ_(M)′ value is 179°, the ΔΨ_(M)′ equals to 178°, which is larger so the present i-value becomes 2.

Once the present i-value is obtained, the resulting i-value and the present Ψ_(M)′ value are substituted to the equation 5 to obtain the present Φ1.

Similar to the method for obtaining the i-value by calculating the plurality of θ_(C)'s from the Ψ_(M)′ value, the j-value also can be obtained by calculating the plurality of Ψ_(C)'s from the θ_(M)′, and the present j-value can be obtained by comparing the present θ_(M)′ value to the previous θ_(M)′ value. Using these known values, the steering angle, Φ2, of the steering shaft can be obtained applying the following equation 6. Φ2=1/r 2(Θ_(M) ′+jΩ)  <Equation 6>

More preferably, the mean value of the Φ1 and Φ2 is used for the steering angle of the steering shaft. In this manner, it is possible to minimize measurement errors in Ψ_(M)′ and θ_(M)′ values.

When the difference between Φ1 and Φ2 is so large that it is greater than a specific value, that means that measurement error exceeds an allowable limit. Therefore, the i-value and the j-value should be recalculated through the procedure shown in FIG. 3 to get new Φ1 and Φ2, and the mean value of Φ1 and Φ2 is obtained therefrom.

In conclusion, according to the present invention, the steering angle can be obtained directly from the i-value and the j-value, without using Ψ−θ. Once the i-value and the j-value are obtained, the following calculation procedure is much simplified.

In other words, once the i-value is obtained, a successive i-value can be obtained simply by comparing the present Ψ_(M)′ value to the previous Ψ_(M)′ value. More importantly, the i-value is not under the influence of measurement error included in the θ_(M)′ value. Moreover, once the i-value is obtained, although the θ_(M)′ value may not be measured because of a mechanical trouble in the angle sensor, the steering angle for the steering shaft can still be measured.

In addition, the present invention can reduce calculation errors found in rounding off steps to define the absolute steering angle (e.g., rounding off ‘k’-value in U.S. Pat. No. 5,930,905 or rounding off an ‘i’-value in U.S. Pat. No. 6,466,889B1). That is, the present invention can resolve a serious error (±1) in the rounding off of the absolute steering angle.

While the invention has been described in conjunction with various embodiments, they are illustrative only. Accordingly, many alternative, modifications and variations will be apparent to persons skilled in the art in light of the foregoing detailed description. The foregoing description is intended to embrace all such alternatives and variations falling with the spirit and broad scope of the appended claims. 

1. A method for measuring an absolute steering angle of a steering shaft for a vehicle using a first rotatable body and a second rotatable body that rotate together with the steering shaft of the vehicle at a predetermined rotation ratio, respectively, the method comprising: obtaining a Ψ_(M)′ value by measuring a relative rotational angle Ψ′ of the first rotatable body and obtaining a θ_(M)′ value by measuring the relative rotational angle θ′ of the second rotatable body, using angle sensors having measurement ranges of Ω; obtaining θ_(C)'s by calculating a plurality of relative rotational angles θ's of the second rotatable body corresponding to the Ψ_(M)′ value, using the relation between the relative rotational angle Ψ′ of the first rotatable body and the relative rotational angle θ′ of the second rotatable body; obtaining a frequency i-value of the first rotatable body by comparing the plurality of θ_(C)'s to the θ_(M)′ value; and obtaining an absolute steering angle Φ1 of the steering shaft based on the relation between Ψ and Φ, after the absolute rotational angle Ψ is obtained by using the i-value.
 2. The method according to claim 1, further comprising: obtaining a present i-value by comparing a previous Ψ_(M)′ value to a present Ψ_(M)′ value, obtaining a present value for the absolute rotational angle Ψ of the first rotatable body, and obtaining a present Φ1 value, which is a successive value of the Φ1 measurement, based on the relation between Ψ and Φ.
 3. The method according to claim 1, further comprising: obtaining a plurality of Ψ_(C)′ values by calculating a plurality of Ψ′ values corresponding to the θ_(M)′ value using the relation between the Ψ′ values and the θ′ values; obtaining a frequency j of the second rotatable body by comparing the plurality of Ψ_(C)′ values to the Ψ_(M)′ value; obtaining an absolute steering angle Φ2 of the steering shaft based on the relation between θ and Φ, wherein the absolute rotational angle θ of the second rotatable body is obtained by using the j-value; and obtaining the steering angle Φ of the steering shaft by taking the mean value of the Φ1 and the Φ2.
 4. The method according to claim 3, further comprising: obtaining a present i-value from a previous i-value after comparing a previous Ψ_(M)′ value to a present Ψ_(M)′ value, obtaining a present value for the absolute rotational angle Ψ from the obtained present i-value, and obtaining a present Φ1 value from a relation between Ψ and Φ; obtaining a present j-value from a previous j-value after comparing a previous θ_(M)′ value to a present θ_(M)′ value, obtaining a present value for the absolute rotational angle θ from the obtained present j-value, and obtaining a present Φ2 value from a relation between θ and Φ; and taking the mean value of the present Φ1 value and the present Φ2 value.
 5. The method according to claim 4, wherein if a difference between the Φ1 value and the Φ2 value, ΔΦ, is greater than a predetermined value, further comprising: reobtaining the i-value of the first rotatable body by comparing a plurality of θ_(C)′ values to a θ_(M)′ value, in which the plurality of θ_(C)′ values are obtained by calculating a plurality of θ's corresponding to a Ψ_(M)′ value based on the relation between the θ′ and the Ψ′; reobtaining a j-value of a second rotatable body by comparing a plurality of Ψ_(C)′ values to a Ψ_(M)′ value, in which the plurality of Ψ_(C)′ values are obtained by calculating a plurality of Ψ's corresponding to a θ_(M)′ value based on the relation between the θ′ and the Ψ′; and taking the mean value of recalculated Φ1 and Φ2 values by using the reobtained i-value and the j-value. 